Hub, in particular for bicycles

ABSTRACT

Bicycle hub includes a shell rotatably supported relative to a hub axle, a rotor rotatably supported by two rotor bearings, and a freewheel device having two interacting freewheel components: a hub-side freewheel component and a rotor-side freewheel component. The freewheel components each include axial engagement elements and are axially movable relative to one another between a freewheel position and an engaging, driving torque position. The hub-side freewheel component includes a threaded axial body section and is screwed into the hub shell. The hub-side freewheel component has an axial, annular surface on which the axial engagement elements are configured. The rolling members of a hub bearing show a defined accommodation inside the hub-side freewheel component to support the shell relative to the hub axle. The hub-side freewheel component includes a tool contour which couples to an adapted tool for releasing the screw connection of the hub-side freewheel component with the shell.

RELATED APPLICATIONS

The present application is a CIP of, and claims 35 USC 120 priority fromSer. No. 15/882,423 filed Jan. 29, 2018, which is a CIP of and claims 35USC 120 priority from U.S. Ser. No. 15/659,830 filed Jul. 26, 2017 andU.S. Ser. No. 15/659,850 filed Jul. 26, 2017, all of which areincorporated by reference.

BACKGROUND

The present invention relates to a hub for at least partiallymuscle-powered vehicles and in particular bicycles, the hub comprising ahub shell which is rotatably supported relative to a hub axle by way oftwo roller bearings disposed on opposite end regions of the hub shell.The hub comprises a rotor for non-rotatable arrangement of at least onesprocket, the rotor being rotatably supported relative to the hub axleby means of at least two rotor bearings. A freewheel device is providedbetween the rotor and the hub shell.

Other than in bicycles, the hub may be used in other partiallymuscle-powered vehicles and two-wheeled vehicles which are for exampleprovided with an electric auxiliary drive. The hub is in particular usedin sports bicycles.

The prior art has disclosed various hubs comprising a freewheel so thatthe pedal crank will not keep rotating along for example during adownhill ride. This freewheel also allows contrarotating of the hubshell and the rotor in backpedaling.

The prior art has disclosed hubs with ratchet freewheels where the pawlscan radially pivot between a freewheel position and an engagingposition. These hubs are provided with different numbers of ratchetpawls and tend to show four ratchet pawls symmetrically distributed overthe circumference. As force is transmitted, the ratchet pawls engage atoothing in the rotor. The relatively low number of ratchet pawlsresults in a relatively large angle of rotation until rotational forceis transmitted when pedalling is resumed.

GB 668,943 has disclosed a freewheel hub for bicycles showing screwedinto the hub shell a shell-shaped part whose inside surface forms theraceway for the ball of the ball bearing, while a radially outwardlyextending wall has an axial toothing formed thereat which together withan axial toothing forms an axial freewheel at the rotor. Due to thelarger number of teeth of the axial toothing, re-engagement is faster aspedaling is resumed. The drawback of this system is that the rotorshifts in the axial direction when the hub is transferred to thefreewheeling state and the engaged state. With the systems used todaythis might cause a gear shift. Moreover, dirt and moisture might enterthe freewheel, impeding or even entirely disabling the function which isdangerous to the rider.

DE 94 19 357 U1 has disclosed a hub with a toothed disk freewheel whichreliably and very quickly transmits the driving force from the rotor tothe hub shell while otherwise, friction losses are relatively low whilethe user does not activate the pedals. A toothed disk freewheel has manyadvantages and allows particular fast response of the freewheel. In thisfreewheel, a pair of toothed disks transmits forward rotational force ofthe rotor while in backpedaling, the teeth disengage axially. The knownhub per se functions satisfactorily and is used in the area of sportsand also in professional riding. However, there is the disadvantage thatthe high loads acting on the hub for example in uphill rides maygenerate bending moments in the hub so as to cause the toothed disk toslightly tilt which results in higher wear on the teeth which aresubjected to higher forces so that durability is limited and the tootheddisks require early replacement to avoid malfunction. DE 10 2010 033 268A1 discloses a hub in which two end-toothed components form an axialfreewheel. Pairs of adjacent hub bearings at the hub shell ends serve assupports relative to the hub axle. The drawback is the high spacerequirement for the adjacent hub bearings. Moreover, the hub axle is notprovided with any radial shoulders so that it cannot serve for axiallysupporting the hub components. Therefore, to axially support the hub theaxial force is transmitted from a roller bearing into the hub shell onone side and on the other side it is abducted through a roller bearingvia sleeve elements disposed on the hub axle. In another embodimentshown in a simplistic illustration, one or two hub bearings areaccommodated on the inside of the end-toothed component and in yetanother embodiment shown in a simplistic illustration, an end toothingof the axial freewheel is integrally formed at the outer bearing race ofthe hub bearing so as to enable saving axial mounting space if only onehub bearing is used. The drawback is, however, that the axial forcesmust again be transmitted radially through the bearing into the hubshell. A freewheel must be configured for rotational forces of up to 400Nm and higher. This means that in the course of operation, theend-toothed component screwed into the hub shell keeps being urged everfurther into the hub shell so as to compress the hub shell. These highloads may result in the hub shell breaking or else the wall thicknessesrequire reinforcing which, however, increases the weight.

Also, hubs with toothed disk freewheels have been disclosed which areprovided with a freewheel having an axial toothing, wherein an axialtoothing is fixedly integrated in the rotor and a toothed disk isnon-rotatably and axially displaceably accommodated in the hub shell bymeans of one or more springs and is axially biased in the directiontoward the toothing in the rotor. Reversely, a hub has been disclosedwhich includes a toothed disk freewheel and has a toothed disk fixedlyintegrated in the hub shell and where the other of the toothed disks isbiased by means of a spring in the direction of the hub shell. Thenagain, both these hub types providing for axial movability of only oneof the toothed disks have the disadvantage due to the high loads insports or professional cycling that some of the teeth are subjected tohigher loads and faster wear so that early replacement on a regularbasis is advisable of the toothed disks, the rotor or even the hub shellto avoid malfunction.

A feasible alternative would be a stiffer configuration overall of a hubwith a toothed disk freewheel by employing stiffer and thus heaviermaterials or by employing greater wall thicknesses which would increasethe weight though. However, since in sports and professional cyclingeach and every gram of weight counts, this does not provide the desiredsolution.

EP 1 121 255 B1 has disclosed a lightweight hub having a toothed diskfreewheel and showing reliable function wherein the teeth of the tootheddisks are stressed more evenly. This hub uses a pair of toothed disks,both of which are axially movable and are axially urged toward oneanother from the outside by means of a spring. The two toothed disks arethus floatingly supported and e.g. in case of the hub flexing or givenother types of stresses they may show better positioning to one anotherso as to provide more even wear on the toothed disks and a particularlyreliable operation. However, an even stiffer hub is desirable.

Against the background of the prior art it is therefore the object ofthe present invention to provide a hub with an axial freewheel whereinthe hub-side freewheel component provides defined accommodation of aroller bearing and which offers enhanced ease of maintenance. The hub isin particular intended to be lightweight or more lightweight andpreferably its configuration is to be stiffer.

SUMMARY

A hub according to the invention is provided for at least partiallymuscle-powered vehicles and in particular bicycles and comprises a hubshell which is rotatably supported relative to (and in particular on) ahub axle (in particular by way of two roller bearings disposed onopposite end regions of the hub shell). The hub comprises a rotorrotatably supported by means of at least two rotor bearings relative toand in particular on the hub axle and particularly preferably disposedfixed or axially stationary in the axial direction in operation tonon-rotatably dispose at least one sprocket. A freewheel device havingtwo interacting freewheel components is comprised namely, a hub-sidefreewheel component and a rotor-side freewheel component. The twofreewheel components each comprise axial engagement elements and theyare movable relative to one another in the axial direction at leastbetween a freewheel position and an intermeshing engaging positionwherein in the engaging position a driving torque can be transmittedfrom the rotor to the hub shell. The hub-side freewheel componentcomprises an axial, threaded body section and is screwed into the hubshell by means of a thread. The hub-side freewheel component comprisesan annular surface on the axially outside surface where the axialengagement elements are formed at least in part. The rolling members ofa hub bearing are located in a defined accommodation within the hub-sidefreewheel component to support the hub shell relative to the hub axle.The hub-side freewheel component comprises at least one tool contourconfigured to be coupled with a matching tool in particular forunscrewing the hub-side freewheel component from the hub shell or elsefor tightening the screw connection.

The hub according to the invention has many advantages. The hubaccording to the invention in particular allows greater ease of mountingand demounting. The hub allows a stiffer architecture than provided inthe prior art while still offering uncomplicated maintenance. Thelaterally axial distance of the roller bearings for supporting the hubshell may be provided considerably larger than in the past. This alsoallows to considerably improve the lateral stiffness of a wheel equippedtherewith.

The rotor and in particular also the hub shell is/are disposed in thesame axial positions both in the freewheel position and in the engagingposition. In the freewheel position the rotor and the hub shell are inparticular decoupled from one another. This means that in the freewheelposition no or an insignificant rotational force is transmitted betweenthe hub shell and the rotor.

The axial engagement elements in particular protrude axially and/or actin the axial direction. The annular surface may be disposed on theaxially outwardly end. The hub-side freewheel component preferablycomprises an annular flange. The annular surface is in particular atleast partially formed on the annular flange. Although the annularflange preferably extends radially, inwardly it may extend radiallyoutwardly as well.

The hub-side freewheel component is a separate part and is notintegrally formed with the hub shell since a hub shell tends to consistof one or more components of a lightweight material or of severallightweight materials such as light metal or fibrous composite materialwhile the freewheel component is at least in part manufactured from (atleast) a/one stronger and thus often heavier material. For example,steel is a suitable material for the freewheel component.

Preferably the hub-side freewheel component comprises (at least) oneappendix projecting outwardly and/or inwardly from the axial bodysection. The appendix may be circumferential in configuration. It isalso possible that multiple finger-like appendices are configured.

In particular, is the tool contour formed by projections and/or recessesprojecting inwardly and/or outwardly. This allows a tool contour toreliably transmit even high rotational forces and reduces the risk ofdamage to the tool or the tool contour.

In advantageous specific embodiments the tool contour is configured atleast partially or entirely by way of a non-round inner or outerperipheral surface or side surface.

It is preferred for the tool contour to comprise two or more contourelements. Contour elements may be different parts and portions ofcomponents such as edges, grooves, toothings, depressions and elevationsetc.

The tool contour comprises in particular two or more through holesand/or two or more blind holes. This combines saving weight withproviding a simple function.

In advantageous configurations at least part of the tool contour isconfigured on the annular flange and/or the appendix. This allowsefficient utilization of radially inwardly and/or radially outwardlyregions. A radially inwardly region is particularly easily accessible.

In particular, at least part of the tool contour is configured on theaxial toothing formed by the engagement elements. For example, singleengagement elements or regions of the axial toothing may be providedwith holes or blind holes for a tool to engage in. Alternately, an innercontour may be provided where parts of the axial toothing are cut out orrecessed, providing a non-round tool contour.

In preferred specific embodiments, the hub comprises a tool having acoupling contour which couples with the tool contour. The couplingcontour may be matched or adapted to the tool contour partially orentirely. The number of contour elements and pertaining link parts maydiffer. Alternately, the number may be the same. What is essential isthat a coupling can be established. The tool may be a standardized toolintended for other purposes.

In particular, are the rolling members of the hub bearing accommodatedin an inner centric receiving space of the axial body section, and theouter ring of the hub bearing is configured on the axial body section oraccommodated therein and in that case in particular pressed in.

In this configuration, the hub-side freewheel component forms a bearingseat which accommodates a roller bearing for defined, rotary support ofthe hub shell. This allows to enlarge by a few millimeters the lateraldistance of the bearings to support the hub shell relative to the hubaxle. This already achieves a considerably increased rigidity of thehub. Any bending moment acting during pedaling is considerablydecreased. The lateral axial distance between the surface of forceapplication for transmitting the driving torque and the bearing positionis considerably shorter than in the prior art since the roller bearingis accommodated radially inwardly of the hub-side freewheel component.The distance may even be halved. Moreover, the lateral axial distance ofthe roller bearings of the hub shell is noticeably increased. The rollerbearings for supporting the hub shell relative to the hub axle may bereferred to as hub shell bearings. At the same time, the outwardlyprotruding appendix on the hub-side freewheel component, which inoperation shows defined abutting against a shoulder in the hub shell,allows to provide a particularly stable and reliable hub. This achievesa sufficiently stable support in the hub shell even when the hub-sidefreewheel component is screwed in. This configuration reliably preventsthe hub-side freewheel component from penetrating ever further into thehub shell in operation.

Another advantage is that the distance between the two rotor bearingsmay also be enlarged so as to achieve increased rigidity there. It isalso very advantageous that the hub is simpler in its architecture. Thehub axle does not require thickening to increase rigidity.

At the same time, the invention allows a clearly more lightweight hubarchitecture overall which is moreover combined with higher rigidity. Aweight advantage is achieved by way of a more lightweight configurationof the hub-side freewheel component. Another weight advantage isachieved by way of configuring the hub shell respectively the hub sleevewith thinner walls. The known prior art provides for the hub shell tosurround the roller bearing and the toothed disk accommodated adjacentthereto in the hub shell. However, a minimum wall thickness of the hubshell must be observed to ensure the required stability. In the knownprior art, this results in a hub shell showing a considerably largerwall thickness over a clearly larger axial region compared to thepresent invention. Thus, the invention achieves higher rigidity combinedwith a lower weight. In addition, the parts required are fewer in numberso as to simplify the architecture and assembly and maintenance. Usingan outwardly protruding appendix moreover distributes the contactpressure of the hub-side freewheel component in the hub shell over alarger diameter and thus achieves a reduced surface pressure. Theradially outwardly protruding appendix prevents the hub-side freewheelcomponent from entering deeper into the hub shell if it is externallythreaded and is screwed into the hub shell.

Axial mounting space is saved by way of the invention. Both the hubshell and also the rotor may be provided with broader axial supportsthan was the case with the prior art known from EP 1 121 255 B1.

Demounting is easy even while the hub-side freewheel component isscrewed into the hub shell so that any rolling members having definedaccommodation therein are no longer directly accessible. A suitable toolrenders demounting easy and uncomplicated.

In the invention, the hub-side freewheel component has an inner andcentral receiving space with a bearing seat and a roller bearingreceived thereat to rotatably support the hub shell so as to stiffen thehub. The invention allows to increase an axial distance of the rollerbearings of the hub shell. The hub shell may overall be supported on aclearly broader basis to thus considerably improve the lateral stiffnessof a wheel equipped therewith.

In a preferred specific embodiment, the two freewheel components arebiased in the engaging position by way of at least one biasing device.The freewheel components preferably each comprise engagement elementsconfigured on the front face which mesh with one another in the engagingposition. In this way, in the engaging position the engagement elementstransmit rotational movement in the driving direction from the rotor tothe hub shell. In the freewheel position, a rotation of the freewheelcomponents is possible relative to one another and thus also of the hubshell relative to the rotor.

In all the configurations, it is preferred for the freewheel componentsto comprise an axial toothing each. The freewheel device is inparticular configured as a toothed disk freewheel. Then, the engagementelements are preferably provided by axial teeth which are in particularbiased to the engaging position by means of at least one spring or aplurality of springs or spring elements. The number of engagementelements on each freewheel component is in particular between 16 and 80and in particular between 18 and 72. This allows very quick responses.

Preferably the rotor-side freewheel component is non-rotatably andaxially movably accommodated on the rotor and the hub-side freewheelcomponent is non-rotatably and also axially fixedly coupled with the hubshell. The rotor-side freewheel component is in particular configuredas, or comprises, a toothed disk and its front face shows an axialtoothing.

In preferred specific embodiments and configurations, the axial bodysection of the hub-side freewheel component respectively at least partof the axial body section is tubular in design and may be referred to asa tubular body section. In preferred configurations the axial or tubularbody section has a round outer cross-section. Then, the round outercross-section is in particular provided with an external thread withwhich the axial (tubular) body section is preferably screwed into aninternal thread of the hub shell when assembled. Then, the axial(tubular) body section is axially fixedly and non-rotatably connectedwith the hub shell. The tubular body section is preferably configuredsubstantially cylindrically.

In preferred embodiments, the axial body section is configured such thatthe axial body section with the outwardly protruding appendix and theannular flange projecting in particular inwardly shows a(n at leastsubstantially) T-shaped cross-section. An S- or Z-shaped cross-sectionis also conceivable. In the case of a T-shaped cross-section thecrossbar of the “T” and thus the annular flange and the appendix arepreferably disposed axially outwardly while the axial or tubular bodysections extend further inwardly into the hub shell respectively intothe hub. This configuration and this e.g. T-shaped cross-section allow acompact structure and high stability under load. The axially outsidesurface (relative to the hub) of the annular flange is equipped with theengagement elements. The axially inside surface (relative to the hub) ofthe appendix provides a stopper which (in the assembled state) restsagainst the radial shoulder in the hub shell. This provides a largervolume of material in the hub shell for reliably transmitting the forcesacting on the hub shell so as to provide a lightweight though stablehub.

This also applies if grooves or cutouts are made in the annular flangeor the appendix to provide a tool receptacle.

The bearing seat is preferably configured on the axial and/or tubularbody section and in particular radially inwardly thereof.

In radial section, the hub-side freewheel component is preferablysubstantially L-shaped in cross-section wherein one of the legs of the“L” forms the axial or tubular body section and the other of the legs ofthe L extends in the radial direction and is equipped with theengagement elements. The cross-section is particularly preferably“T”-shaped wherein the annular flange and the appendix are axiallyoverlapping or at least approximately located in the same axialposition.

Preferably, the hub-side freewheel component accommodates more than ⅔ ofthe axial width of the roller bearing. In particular, a substantialrespectively the most substantial part of the roller bearing shows adefined accommodation on the bearing seat of the hub-side freewheelcomponent. Preferably, the hub-side freewheel component accommodatesmore than 50% and particularly preferably more than 75% of the axialwidth of the roller bearing. In preferred configurations, the hub-sidefreewheel component accommodates between approximately 80% and 90% orbetween 80% and 99.5% and in particular between 90% and 99.5% of theaxial width of the roller bearing. Preferably, there is a clear distance(in the axial direction) between the axially inwardly front face of theaxial body section and the hub shell. The clear distance generates aplay between the axially inwardly front face of the axial body sectionand the hub shell and it is in particular larger than 0.02 mm andpreferably it is between 0.03 mm and 1.5 mm, in particular between 0.05mm and 0.6 mm and preferably between 0.08 mm and 0.35 mm. In preferredconfigurations, the clear distance is between 0.5% and 5% of the axiallength of the roller bearing accommodated on the hub-side freewheelcomponent. The clear distance leads to an axial position of the axialbody section defined by the radially outwardly protruding appendix andto preventing the axial body section from screwing in ever further. Theradially outwardly protruding appendix of the hub-side freewheelcomponent in particular protrudes radially outwardly beyond the axialbody section and when mounted it rests against the radial shoulder ofthe hub shell. This achieves an axially defined position of the hub-sidefreewheel component. The outwardly protruding appendix may be configuredas a singular appendix or else several appendices are provided(symmetrically) distributed over the circumference. The appendicestogether with the cutouts in-between then form a tool contour for inparticular form-fit engagement of a tool. Or else the appendix may beconfigured as a circumferential flange which extends radially outwardlyin particular from the axially outwardly end of the axial body section.

The hub-side freewheel component comprises an annular flange the frontface of which is provided with the engagement elements (axiallyoutwardly). The annular flange in particular extends radially inwardlyon the axially outwardly end of the axial body section. Then, theannular flange forms the inwardly projecting radial leg of the T or an Las it has been described above.

Preferably a radial bearing shoulder is formed in the hub shell fordefined axial alignment of the roller bearing accommodated in thehub-side freewheel component. The roller bearing is in particulardisposed in an axially defined position between the radial bearingshoulder in the hub shell and the annular flange. Preferably, a definedplay is provided on one axial side and on the other axial side theroller bearing is disposed without play. A disadvantageousoverdefinition is thus prevented. Preferably, a free distance is formedbetween the roller bearing accommodated in the hub-side freewheelcomponent and the axially inside surface of the annular flange. The freedistance provides for axial play. The free distance is in particularlarger than 0.02 mm or 0.05 mm. The free distance is preferably largerthan 0.1 mm or larger than 0.2 mm and may be up to and larger than 0.5mm or 1 mm. The free distance is provided in particular between theaxially inside surface of the annular flange and the outer ring of thefreewheel-side roller bearing for the hub shell. In a preferredconfiguration, the free distance is between 0.02 mm and 0.35 mm.

The outer ring of the freewheel-side roller bearing of the hub shellbears against the radial bearing shoulder in the hub shell in particularwith its axially further inwardly end so as to cause defined alignmentof the roller bearing. Particularly, preferably a clear distance (in theaxial direction) is present between the axially inwardly front face ofthe axial body section and the hub shell, and a free distance is formedbetween the roller bearing accommodated in the hub-side freewheelcomponent and the axially inside surface of the annular flange.Preferably, the clear distance and the free distance are approximatelythe same. Due to existing tolerances of component parts andmanufacturing and mounting tolerances the clear distance and the freedistance may be configured different. The clear distance and the freedistance each prevent an overdefinition in the mounted hub.

In advantageous configurations the biasing device is accommodated in therotor-side freewheel component. The biasing device is in particularsubstantially entirely and particularly preferably entirely accommodatedinwardly of the rotor-side freewheel component. This offers considerableadvantages as regards the axial mounting space since the rotor-sidefreewheel component does not, or only very little, extend in the axialdirection so as to allow saving axial mounting space. This allows tofurther increase the hub rigidity.

The rotor-side freewheel component in particular comprises an inparticular cylindrical guide section having a non-round outer contourmeshing with an adapted non-round inner contour in the rotor to enableaxial movability of the rotor-side freewheel component relative to therotor and to provide the non-rotatable coupling between the rotor andthe rotor-side freewheel component.

In preferred configurations, the front face end of the rotor-sidefreewheel component is configured as a washer with the engagementelements disposed thereat (on the front face).

Preferably, the rotor-side freewheel component with the guide sectionand the washer disposed on the front face end shows a cross-sectionapproximately L-shaped in the radial direction. An axially aligned legis formed by the guide section. A radially aligned leg is formed by thefront-face washer.

Preferably, the biasing device urges the front-face washer with theengagement elements in the direction of the hub-side freewheelcomponent. Then, the biasing device preferably rests against the insideof the washer.

The washer and the (cylindrical) guide section preferably substantiallyform the rotor-side freewheel component. The guide section and thewasher are particularly preferably manufactured integrally.

Particularly preferably, the biasing device is axially supportedoutwardly (immediately) against a rotor bearing to rotatably support therotor. Then, the biasing device is particularly preferably directly andimmediately supported on an outer bearing ring of the rotor bearing.

In all the configurations, the bearings for supporting the hub shell andthe rotor bearings for supporting the rotor are preferably configured asroller bearings, and in particular as deep-groove ball bearingscomprising an outer bearing ring (also referred to as outer ring), aninner bearing ring (also referred to as inner ring) and in-between,rolling members disposed in particular in a rolling member cage.

The biasing device may be indirectly supported on a rotor bearing forexample if a disk is disposed between the rotor bearing and the biasingdevice. Supporting the biasing device immediately on the rotor bearingallows a particularly space-saving architecture, at any rate with thebiasing device configured as a cylindrical coil spring. In otherconfigurations it is also possible to employ a number of single springswhich are supported on the outside of the rotor bearing or othercomponents.

Preferably, a sealing device is provided between the rotor and the hubshell. The sealing device in particular comprises a non-contactlabyrinth gap diverting at least once. Furthermore, the sealing devicepreferably comprises at least one contacting sealing lip in particulardownstream of the labyrinth gap. The sealing device in particularprevents access of water and dust to the freewheel device as extensivelyas possible and in particular the most extensively possible. The sealinglip is preferably provided radially further inwardly than the labyrinthgap.

In all the configurations, it is particularly preferred for the rotorand preferably the hub to be provided for largely or completely no-toolsdismantling. The hub shell is preferably plugged, the limit stops are inparticular plugged on (inserted or preferably pushed on) and the hubis—optionally apart from the hub-side freewheel component—preferablyprovided for entirely no-tools dismantling. The hub-side freewheelcomponent may likewise be provided for no-tools dismantling. Thisfacilitates assembly and dismantling and thus also maintenance orrepairs.

When assembled, a clamping force of the hub is preferably supported viathe inner rings of the roller bearings of the hub shell and the innerrings of the rotor bearings. In particular, at least one sleeve bodyeach is disposed for form-fit force transmission of the clamping force,between the freewheel-side roller bearing of the hub shell and thefreewheel-side rotor bearing and between the two rotor bearings. In thisway, a form-fitting and particularly stable hub is provided.

Preferably two and in particular exactly two radial bulges areconfigured on the hub axle. The two radial bulges are preferablyconfigured in the region of the roller bearings to support the hubshell. Preferably, the radial bulges show on the axially inwardly face a(continuous or gradual or stepless or stepped) increase of the wallthickness and a shoulder each is configured on the axially outwardlyside. These shoulders may serve as stoppers for the inner bearing cup ofthe roller bearings to support the hub shell. Optionally, a spacer suchas a disk or a sleeve may be inserted between the stopper and the rollerbearing. In all of these configurations, forces may be transmittedthrough the hub axle and the spacers such as disks, sleeve bodies andinner bearing cups of the roller bearings.

Particularly preferably, the hub axle is configured cylindrical and,other than the radial bulges against which the roller bearings rest tosupport the hub shell, it shows a substantially constant diameter and asubstantially constant wall thickness wherein the diameter and the wallthickness vary by less than 25% and preferably less than 15%. Theinterior of the hub axle is particularly preferably cylindrical inconfiguration.

Preferably, the roller bearings disposed on the opposite end regions ofthe hub shell rest axially inwardly with their respective inner ringsagainst radial bulges of the hub axle. The hub axle is thus employed forform-fit force transmission.

Particularly preferably, at least one of the roller bearings and/or therotor bearings is configured as a deep-groove ball bearing and inparticular as a commercially available and/or standardized deep-grooveball bearing. At least one of the roller bearings and/or the rotorbearings is preferably provided with a rolling member cage and/orbearing seals directly attached to the roller bearing and preventingentry of water and/or dust into the interior of the roller bearing.

In all the configurations it is preferred for the hub to be designed foruse with a through axle. Preferably, the hub comprises a through axle.

It is preferred to provide limit stops which are pushed onto the axle orhub axle or inserted into the hub axle. It is possible to provideexchangeable limit stops with one set of limit stops configured toaccommodate a through axle and another set of limit stops provided toaccommodate for example a quick release. The latter set of limit stopsshows axially outwardly cylindrical shoulders which are configured to bereceived in the dropouts of a frame and whose outer diameter ispreferably smaller than an inner diameter of the hub axle in a centralregion of the hub axle When the hub is delivered with two sets of limitstops, the user may choose whether to use them with the through axle orwith a quick release. Later retrofitting is also possible.

All the configurations may be provided with more than two rollerbearings to support the hub shell. Then, at any rate (at least) oneroller bearing is disposed on each of the two end regions. More than tworotor bearings may likewise be employed.

Further advantages and features of the present invention can be takenfrom the exemplary embodiments which will be discussed below withreference to the enclosed figures.

BRIEF DESCRIPTION OF THE DRAWINGS

The figures show in:

FIG. 1 a schematic illustration of a mountain bike;

FIG. 2 a schematic illustration of a racing bicycle;

FIG. 3 a section of a hub according to the invention;

FIG. 4 an enlarged detail of the section in FIG. 3;

FIG. 5 a perspective illustration of the hub-side freewheel component;

FIG. 6 a section of the hub-side freewheel component according to FIG.5;

FIG. 7 an exploded view of the hub according to FIG. 3;

FIG. 8 a section of another hub according to the invention;

FIG. 9 a perspective illustration of the hub-side freewheel component ofthe hub according to FIG. 8;

FIG. 10 a section of the hub-side freewheel component according to FIG.9;

FIG. 11 a top view of another hub-side freewheel component;

FIG. 12 a schematic view of a fitted tool;

FIG. 13 a perspective view of another hub-side freewheel component; and

FIG. 14 a top view of the hub-side freewheel component according to FIG.13 with a pertaining tool shown in section.

DETAILED DESCRIPTION

The FIGS. 1 and 2 illustrate a mountain bike or racing bicycle 100respectively which are equipped with a hub 1 according to the invention.The mountain bike or racing bicycle 100 is provided with a front wheel101 and a rear wheel 102. The hub 1 according to the invention is usedwith the rear wheel 102. The two wheels 101, 102 are provided withspokes 109 and a rim 110. Conventional caliper brakes or other brakessuch as disk brakes may be provided.

A bicycle 100 comprises a frame 103, a handlebar 106, a saddle 107, afork or suspension fork 104 and in the case of the mountain bike, a rearwheel damper 105 may be provided. A pedal crank 112 with pedals servesfor driving. Optionally the pedal crank 112 and/or the wheels may beprovided with an electrical auxiliary drive. The hubs 1 of the wheelsmay be attached to the frame by means of a through axle 25 or a quickrelease 49.

FIG. 3 shows in a section the hubs 1 inserted in the rear wheels 102 inthe bicycles according to FIGS. 1 and 2.

The hub 1 according to the invention comprises a hub shell 2 which isrotatably supported in the axial end regions 3 and 4 by means of theroller bearings 24 respectively 14 to be rotatable relative to, andpresently immediately on, a hub axle 5. This means that the rollerbearings 14, 24 are each directly disposed on the hub axle 5.

The hub furthermore comprises a rotor 8 on which to dispose at least onesprocket. In particular, a sprocket cluster may be pushed on andattached or arranged. A freewheel device 9 is provided between the rotor8 and the hub shell 2, comprising the hub-side freewheel component 10and the rotor-side freewheel component 20. To prevent penetration ofwater and dust into the interior of the hub 1 and in particularadmission of water and dust to the freewheel device 9, a sealing device38 is configured between the rotor 8 and the hub shell 2 comprising alabyrinth-like sealing gap and a downstream lip seal contacting therotor and reliably protecting the freewheel from entry of dirt andwater.

Limit stops 39 and 40 are pushed onto the two ends of the hub axlewhich—while the wheel equipped therewith is not clamped in the frame—aresecured on the hub axle by way of O-rings 48. The limit stops 39 and 40are each provided with a sealing flange 46 or 47 protecting the ends ofthe hub 1 from entry of dirt and water. This rotor-side limit stop 40 isprovided with a radial sealing flange 47 while the other limit stop 39is provided with a double flange 46 consisting of a pair of radialsealing flanges between which an axial distance and free space isformed.

The roller bearings 14, 24 for rotatably supporting the hub shell 2 reston radial shoulders in bulges 43, 44 of the hub axle 5. The bulges 43and 44 are each located axially inwardly of the bearings 14, 24.

In all the configurations of the hub 1 the bulges 43, 44 preferably showa somewhat larger radial wall thickness of the hub axle 5. Inparticular, is the radial wall thickness in this region between about1.5 times and 3 times the radial wall thickness in the other regions.Other than the bulges 43, 44 the hub axle 5 is substantially a hollowcylinder in configuration and shows differences in the wall thickness ofpreferably less than 25% and in particular less than 15% or less than10% or less than 5% or less than 2%. Preferably, a relationship of themaximum outer diameter of the hub axle (incl. bulge) to the minimuminner diameter of the hub axle is less than 2.0 and in particular lessthan 1.75 and preferably less than 1.6. Preferably, the relationship ofthe maximum outer diameter of the hub axle to the minimum inner diameterof the hub axle is larger than 1.25 and in particular larger than 1.4.

The rotor 8 is rotatably (and immediately) supported on the axle 5 bymeans of a pair of rotor bearings 6 and 7.

The roller bearing 14 is accommodated inwardly of the hub-side freewheelcomponent 10 in a central receiving space 11 in a defined location,presently pressed-in, on a bearing seat 12. This allows to saveconsiderable axial mounting space so that the stability and rigidity ofthe hub can be increased. Moreover, the total weight of the hub 1 isconsiderably reduced. Both the weight of each of the freewheelcomponents and the weight of the hub shell can be reduced since the wallthickness in the rotor-side end region 4 of the hub shell 2 can bereduced.

FIG. 4 shows an enlarged detail from FIG. 3, with the freewheel device 9once again shown in the engaging position 31, in which the engagementelements 33 (see FIGS. 5 and 6) designed in particular as axialtoothings 10 d, 20 d, of the freewheel component 10 and the freewheelcomponent 20 are in non-rotatable engagement with one another. Theengagement elements 33 are configured such (see for example FIG. 5) thatgiven a rotational direction in the driving direction a rotational forceis reliably transmitted to the hub shell 2 while given an oppositerotational direction the freewheel component 20 is urged axiallyoutwardly counter to the biasing force of the biasing device 32 untilthe engagement elements 33 disengage so as to enable a rotation of therotor relative to the hub shell. The hub-side freewheel component 10comprises an axial body section 13 provided with a thread 10 c. Thehub-side freewheel component 10 has an annular surface 18 d. The annularsurface 18 d is in particular provided on the axially outside surface 18b of the annular flange 18. Then, this is where the axial engagementelements 33 of the axial toothing 10 d are configured.

The rotor-side freewheel component 20 is provided with a guide section23 showing a non-round outer contour 21. The non-round outer contour 21meshes with a matching, non-round inner contour 37 in the rotor 8 and isaxially displaceable in parallel to the axial direction 30 in the rotor8.

This freewheel component 10 shows an approximately T-shapedconfiguration in radial cross-section. The freewheel component 10 isaxially fixedly and (in the driving direction) non-rotatably connectedwith the hub shell 2.

A cylindrical bearing seat 12 is formed radially inwardly of the axialbody section where the rotor-side roller bearing 14 is accommodated torotatably support the hub shell 2. When the roller bearing 14 is mountedit is form-fittingly accommodated in the axial direction with its innerring between the bulge 44 and the sleeve body 41. The rolling members 53of the roller bearing or hub bearing 14 show a defined accommodationinside the hub-side freewheel component 10 to support the hub shell 2relative to the hub axle 5. This rolling member 53 is inserted directlyinto the hub shell and preferably pressed in. This is to ensure definedaccommodation.

As will be discussed with reference to the FIGS. 5 to 7, the hub-sidefreewheel component 10 comprises at least one tool contour 70 whichcouples to an adapted tool 80 to provide for ease of releasing the screwconnection of the hub-side freewheel component 10 from the hub shell 2.During riding the hub-side freewheel component 10 tightens automaticallyand in the counterrotation direction the freewheel automaticallydisengages due to the axial toothings. This is why a tool contour 70considerably facilitates mounting and demounting.

The force-fit is effected in the axial direction 30 from the limit stop40 via the inner ring of the rotor bearing 7, the sleeve body 42, theinner ring of the rotor bearing 6, the sleeve body 41, the inner ring ofthe roller bearing 14 and it is then introduced via the radial bulge 44into the hub axle 5 from where it is transmitted via the radial bulge 43to the inner ring of the roller bearing 24 from where the clamping forceis ultimately dissipated via the limit stop 39.

In the mounted state the appendix 17 of the hub-side freewheel component10 protruding outwardly and in this exemplary embodiment configuredcircumferentially rests against a radial shoulder 35 within the hubshell 2. The position of the hub-side freewheel component 10 is definedby the radial shoulder 35 in the hub shell.

The roller bearing 14 for supporting the hub shell is accommodated onthe bearing seat 12 in the central receiving space 11 and takes adefined position in the hub shell 2 in the axial direction by way of theinner surface 19 of the annular flange 18 of the hub-side freewheelcomponent 10 and the radial bearing shoulder 36. There is preferably asmall axial play between the inner surface 19 of the annular flange 18and the outer ring 50 of the roller bearing 14 while the roller bearing14 rests against the radial bearing shoulder 36 in the hub shell 2without play.

The roller bearing 14 preferably has a sealing unit 57 for sealing theroller bearing. Likewise, the other roller bearing 24 and the rotorbearings 6 and 7 are preferably each provided with such sealing units 57for sealing on both sides.

The rotor-side freewheel component 20 comprises on its front face 22 awasher 28 on which the engagement elements 33 are configured. The washer28 is in particular configured integrally with a cylindrical guidesection 23 of the rotor-side freewheel component 20. In the interior ofthe freewheel component 20 the biasing device 32 configured inparticular as a coil spring preferably presses against the front faceinner surface 29 so that the freewheel component 20 is biased in theengaging position 31. The coil spring 32 is supported at the other endpreferably on the outer ring of the rotor bearing 6. This achieves aminimum axial mounting space whereby the rigidity of the hub can bemarkedly increased overall.

As is illustrated in FIG. 3, an axial distance 26 between the rollerbearings 14 and 24 for rotatably supporting the hub shell is achievedwhich is clearly larger than in the prior art. This allows toconsiderably increase the rigidity and stability of the hub. Thisconsiderable increase of the axial distance 26 by several millimetersallows to eliminate a double-end, floating axial support of thefreewheel components 10 and 20 while still providing increased rigidityof the hub. The freewheel components 10, 20 which are in particularconfigured as toothed disks show even wear and a safe function isachieved. Moreover, the weight of the hub can be clearly reduced.Compared to the prior art the axial distance 26 between the inner ringsof the roller bearings for supporting the hub shell can be enlarged bymore than 5 or even 6 mm. The axial distance 27 between the rotorbearings may likewise be increased by more than 1 mm so that thestability under load of the hub 1 increases and the lateral stiffnesscan be considerably increased.

FIGS. 5 and 6 show the hub-side freewheel component 10 in a perspectiveview and in section. It is apparent that the hub-side freewheelcomponent allows a compact architecture. The annular appendix 17 allowsa defined axial positioning of the hub-side freewheel component 10 inthe hub shell 2. The engagement elements 33 are formed on the axiallyoutside surface 18 b on the front face 22 of the annular flange 18 whichextends radially inwardly in particular from the axial and presentlytubular body section 13.

In FIG. 5, one can recognize the tool contour 70 respectively theprojections 71 and the recesses 73 of the tool contour 70. This toolcontour 70 is configured on the annular surface 18 d on the annularflange 18 and comprises projections projecting radially inwardly orviewed relative thereto, recesses 73 projecting outwardly. The toolcontour 70 on the whole forms a non-round peripheral surface 75 which isactuated by a suitable tool. The tool contour 70 may, as in this case,comprise two or more contour elements 71, 73.

In radial cross-section, the approximately T-shaped structure 45 of thehub-side freewheel component 10 can be seen where the bearing seat 12 isformed radially inwardly where the roller bearing 14 shows a definedaccommodation. The tool contour 70 is provided on the annular flange 18.

The roller bearing 14 has an axial width 16 and is supported in theaxial body section 13 on the bearing seat 12 over the length 18 a acrossthe majority, presently between 80% and 90%, of its axial width. Thefact that the roller bearing 14 protrudes somewhat axially inwardly maymoreover ensure a precisely defined axial arrangement. An axialoverdefinition is avoided.

The roller bearing 14 has an outer ring 50 and an inner ring 52 betweenwhich the rolling members 53 are disposed in guide grooves 56. Sealingunits 57 seal the roller bearing 14 in both axial directions.

For better clarity the illustration of the roller bearing 14 was omittedin the bottom part of FIG. 5. When the roller bearing 14 is installed itis axially secured in the hub shell by the freewheel component 10screwed into the hub shell.

FIG. 7 shows an illustration of essential parts of the hub 1 accordingto the invention. On the left, the limit stop 39 is shown which afterinstallation or insertion of the roller bearing 24 into the hub sleeve 2can be pushed onto the hub axle 5. The hub axle 5 shows radial bulges 43and 44. On the rotor side of the hub shell 2, the roller bearing 14 isaccommodated on the bearing seat 12 of the hub-side freewheel component10 and is screwed into the hub shell 2 together with the freewheelcomponent 10. Thereafter, the sealing device 38 is inserted and thesleeve body 41 is pushed on.

An adapted or adjustable tool 80 is used for releasing as isschematically illustrated in the FIG. 12 or 14. This tool comprises atleast two fingers or engaging dogs projecting outwardly and meshing withthe recesses 73. A non-rotatable connection for mounting or demountingcan thus be established.

The rotor bearings 6 and 7 with the sleeve body 42 in-between areinserted into the rotor 8. The biasing device 32 and the rotor-sidefreewheel component 20 are inserted into the rotor 8 and the rotor 8 ispushed onto the hub axle 5. Finally, the limit stop 40 is pushed on.

The FIGS. 8 to 10 illustrate a slightly modified exemplary embodiment.The reference numerals are identical so that the description of theprevious exemplary embodiment may be referred to identically, apart froma few deviating parts, and it serves again to describe this exemplaryembodiment. Substantial differences and the substantial parts deviatingfrom the preceding exemplary embodiment will be discussed below.

FIG. 8 shows a section of the complete hub, FIG. 9 shows a perspectiveillustration of the hub-side freewheel component 10 and FIG. 10 shows asection of FIG. 9.

Unlike in the previous exemplary embodiment this hub 1 is not providedwith radially circumferential spoke flanges but the hub 1 is equippedwith accommodations for mounting so-called “straight pull” spokes. Thenthe hub shell may be configured accordingly to accommodate e.g.straight, non-cranked spokes (“straight pull spokes”). However, the hub1 according to FIG. 8 may be equipped as is the hub 1 according to FIG.3, with conventional and circumferential spoke flanges or the like.

The tool contour 70 shown is configured on the outwardly projectingappendix 17 and again consists of projections 72 and recesses 74. Theperipheral surface 75 respectively the ensuing cutouts may be used withan adapted tool 80 for non-rotatable coupling. In a simple case therecesses are mill-cut from the originally circumferential appendix 17.Two, three, four, five, six or more projections and recesses may beprovided. The number of coupling parts may—though it does not needto—correlate therewith.

Another difference to the hub 1 according to FIG. 3 is that both FIG. 8and FIG. 10 explicitly show a recognizable, free distance 16 a. The freedistance 16 a provides sufficient axial play. The roller bearing 14accommodated in the freewheel component 10 rests against the axiallyinwardly end 14 a showing the outer bearing ring respectively outer ring50 on the bearing shoulder 36 in the hub shell 2 to provide definedalignment of the roller bearing 14.

The axially outwardly end 14 b of the roller bearing 14 shows the freedistance 16 a respectively the play or the gap between itself and theaxially inside surface 18 c of the annular flange 18. The free distance16 a is in particular larger than 0.01 mm and it is preferably more than0.1 mm, in particular approximately 0.2 mm. The exemplary embodimentaccording to FIG. 3 also comprises a (narrower) free distance 16 a whichis not recognizable in the scale of the drawing.

FIG. 10 shows the stopper 17 d formed on the axially inside surface 17 cof the appendix 17. In the mounted state the stopper 17 d rests againstthe radial bearing shoulder 36 in the hub shell. The stopper 17 dtogether with the radial bearing shoulder 36 prevents the hub-sidefreewheel component from screwing ever further into the hub shell 2.Absent such boundary, any rotational force acting on the axial toothingwill over time result in ever increasing screwing in. Thus, absent thestopper 17 d, the hub shell may be dilated and even burst since thefreewheel is configured for transmitting rotational forces of up to 400Nm or more.

Another contribution is due to the clear distance 13 b which isconfigured (in the axial direction) between the axially inwardly frontface of the axial body section and the hub shell and is presentlybetween approximately 0.08 mm and 0.35 mm. This is to ensure that theaxial body section 13 screws into the hub shell up to the stopper 17 dwhere it is supported on the hub shell.

FIG. 11 shows another embodiment of a hub-side freewheel component 10,specifically a top view of the axially outwardly front face. Thehub-side freewheel component 10 in turn is provided with an axialtoothing 10 d with engagement elements 33 on the annular surface 18 d,the region of the axial toothing 10 d being provided with through holesor preferably blind holes 76 providing a tool contour 70. In this case,six blind holes 76 distributed symmetrically are provided. Alternately,more or less holes may be provided, and a symmetric distribution of theblind holes 76 is not required.

FIG. 12 schematically shows a tool 80 for the embodiment according toFIG. 11 wherein finger-like projections or pins are provided forcoupling parts 81. This tool is provided with a shaft 82 and e.g. ahandle 83. This is where a connection such as a cross hole may beconfigured through which a rod may be passed so as to allow applying alarger rotational force.

FIG. 13 shows another embodiment of a hub-side freewheel component 10 ina perspective illustration and FIG. 14 shows a top view with the tool 80applied.

In this case, the tool contour 70 is formed by a polygonal, presentlyhexagonal cutout provided radially inwardly. The tool 80 in FIG. 14 isconfigured correspondingly matching so as to allow form-fit insertion.

In all the cases it is possible for at least part of the tool contour 70to be configured on the annular flange 18 (as in this case) and/or onthe appendix 17.

The tool 80 may be enclosed to the hub 1 to provide ease of mounting anddemounting.

Dismantling and maintenance of the hub 1 is accordingly simple and maybe performed manually anytime to clean the hub after use for example inoff-road terrain or following an extended road ride. This enables toensure an always reliable function.

The hub enables increased lateral stiffness, increased bendingstiffness, and a still safe operation. At the same time, the weight maybe reduced which is of particular importance in the area of sports andfor professional use.

Another advantage is the smaller cross-section of the hub shell which isthus aerodynamically better. The quantity of parts is smaller so as tomake servicing, assembly and disassembly easier. Manufacturing the hubis also easier.

In all the configurations, it is preferred to employ ground innerbearing rings in the roller bearings. A ground outer ring may also beemployed so as to obtain very low frictional values.

While a particular embodiment of the present invention has beendescribed herein, it will be appreciated by those skilled in the artthat changes and modifications may be made thereto without departingfrom the invention in its broader aspects and as set forth in thefollowing claims.

List of reference numerals:  1 hub  2 hub shell  2c thread, internalthread 3, 4 end region  5 hub axle 6, 7 rotor bearing  8 rotor  9freewheel device 10 hub-side freewheel component  10c thread, internalthread  10d axial toothing 11 receiving space 12 bearing seat 13 axialbody section  13a axially inwardly front face  13b clear distance 14roller bearing  14a axially inwardly end  14b axially outwardly end 16axial width  16a distance 17 appendix  17c axially inside surface  17dstopper 18 annular flange  18a length of 18  18b axially outside surface 18c axially inside surface  18d annular surface 19 inner surface of 1820 rotor-side freewheel component  20d axial toothing 21 outer contour22 front face of 10, 20 23 cylindrical guide section 24 roller bearing25 through axle 26 bearing distance 14, 24 27 bearing distance 6, 7 28washer 29 inner surface of 28 30 axial direction 31 engaging position 32biasing device 33 engagement elements 35 radial shoulder in 2 36 radialbearing shoulder in 2 37 inner contour in 8 38 sealing device 39, 40limit stop 41, 42 sleeve body 43, 44 radial bulges 45 T-shape 46 doubleflange of 39 47 sealing flange of 40 48 O-ring 49 quick release 50 outerring of 14 51 outer ring of 24 52 inner ring 53 rolling member 55raceway at 50 56 guide groove 57 sealing unit 58 seal ring 60 outer ringof 6, 7 61 inner ring of 6, 7 70 tool contour 71, 72 projection 73, 74recess 75 peripheral surface 76 blind hole 77 contour element 80 tool 81coupling part 82 shaft 83 grip member 84 coupling contour 100  bicycle101  wheel, front wheel 102  wheel, rear wheel 103  frame 104  fork,suspension fork 105  rear wheel damper 106  handlebar 107  saddle 109 spoke 110  rim 112  pedal crank

1. A hub for at least partially muscle-powered vehicles and inparticular bicycles comprising: a hub shell which is rotatably supportedrelative to a hub axle, a rotor rotatably supported relative to the hubaxle by at least two rotor bearings, and a freewheel device having twointeracting freewheel components namely, a hub-side freewheel componentand a rotor-side freewheel component; wherein the two freewheelcomponents each comprise axial engagement elements and are movablerelative to one another in the axial direction at least between afreewheel position and an intermeshing engaging position, wherein in theengaging position a driving torque can be transmitted in the directionof drive rotation, wherein the hub-side freewheel component comprises anaxial body section which is provided with a thread and is screwed intothe hub shell by means of a thread and wherein the hub-side freewheelcomponent comprises an axial annular surface on which the axialengagement elements are formed at least in part; and the rolling membersof a hub bearing show a defined accommodation inside the hub-sidefreewheel component to support the hub shell relative to the hub axle,and that the hub-side freewheel component comprises at least one toolcontour which couples to an adapted tool in particular for releasing thescrew connection of the hub-side freewheel component with the hub shell.2. The hub according to claim 1, wherein the hub-side freewheelcomponent comprises an annular flange wherein the annular surface is atleast partially configured on the annular flange.
 3. The hub accordingto claim 1, wherein the hub-side freewheel component comprises anappendix protruding outwardly from the axial body section.
 4. The hubaccording to claim 1, wherein the tool contour is formed by projectionsand/or recesses projecting inwardly or outwardly.
 5. The hub accordingto claim 1, wherein the tool contour is formed by a non-round peripheralsurface.
 6. The hub according to claim 1, wherein the tool contourcomprises two or more contour elements.
 7. The hub according to claim 1,wherein the tool contour comprises two or more through holes and/orblind holes.
 8. The hub according to claim 1, wherein at least part ofthe tool contour is configured on the annular flange and/or theappendix.
 9. The hub according to claim 1, wherein at least part of thetool contour is configured on the axial toothing formed by theengagement elements.
 10. The hub according to claim 1, wherein therolling members of the hub bearing are accommodated in an inner centricreceiving space of the axial body section and the outer ring of the hubbearing is configured or accommodated on the axial body section.
 11. Thehub according to claim 1, wherein the axial body section with anoutwardly protruding appendix and an inwardly projecting annular flangeshows a T-, S-, or Z-shaped cross-section.
 12. The hub according toclaim 1, wherein the hub-side freewheel component accommodates more than⅔ of the axial width of the roller bearing.
 13. The hub according toclaim 1, wherein a radial bearing shoulder is formed in the hub shellfor defined axial alignment of the roller bearing accommodated in thehub-side freewheel component.
 14. The hub according to claim 1, whereina free distance is configured between the roller bearing accommodated inthe hub-side freewheel component and the axially inside surface of theannular flange and/or wherein a clear distance is configured between aninner axial front face of the axial body section and the hub shell. 15.The hub according to claim 1, comprising a tool showing a couplingcontour which couples with the tool contour.